US7670120B2 - Scroll-type refrigerant compressor having fluid communication between lubrication duct and return duct - Google Patents

Scroll-type refrigerant compressor having fluid communication between lubrication duct and return duct Download PDF

Info

Publication number
US7670120B2
US7670120B2 US11/920,979 US92097906A US7670120B2 US 7670120 B2 US7670120 B2 US 7670120B2 US 92097906 A US92097906 A US 92097906A US 7670120 B2 US7670120 B2 US 7670120B2
Authority
US
United States
Prior art keywords
shaft
compressor
oil
duct
lubrication
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related, expires
Application number
US11/920,979
Other versions
US20090041602A1 (en
Inventor
Pierre Ginies
David Genevois
Jean De Bernardi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Danfoss Commercial Compressors SA
Original Assignee
Danfoss Commercial Compressors SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Danfoss Commercial Compressors SA filed Critical Danfoss Commercial Compressors SA
Assigned to DANFOSS COMMERCIAL COMPRESSORS reassignment DANFOSS COMMERCIAL COMPRESSORS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DE BERNARDI, JEAN, GENEVOIS, DAVID, GINIES, PIERRE
Publication of US20090041602A1 publication Critical patent/US20090041602A1/en
Application granted granted Critical
Publication of US7670120B2 publication Critical patent/US7670120B2/en
Expired - Fee Related legal-status Critical Current
Adjusted expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S418/00—Rotary expansible chamber devices
    • Y10S418/01—Non-working fluid separation

Definitions

  • the subject of the present invention is a cooling spiral compressor.
  • a spiral compressor also known as a scroll compressor, comprises a sealed enclosure delimited by a shell containing a suction volume and a compression volume separated by a compression stage, and placed respectively on the sides of the two ends of the enclosure.
  • An electric motor is placed in the suction volume, with a stator situated on the outside, mounted fixedly relative to the shell, and a rotor placed in a central position, fixedly attached to a drive shaft or crank shaft.
  • the drive shaft comprises an out-of-alignment lubrication duct extending over the whole length of the latter, supplied with oil contained in a casing situated in the bottom portion of the enclosure by an oil pump placed at a first end of the shaft.
  • the lubrication duct comprises lubrication orifices at the various guide bearings of the shaft.
  • the compression stage contains a fixed volute fitted with a spiral engaged in a spiral of a movable volute, the two spirals delimiting at least one compression chamber of variable volume.
  • the second end of the drive shaft is fitted with an eccentric driving the movable volute in an orbital motion, to compress the aspirated refrigerant gas.
  • the shell delimiting the sealed enclosure comprises a refrigerant gas inlet.
  • This inlet opens into the annular volume arranged between the motor and the shell. From a practical point of view, gas arrives from outside and enters this annular space. One portion of the gas is directly sucked in the direction of the compression stage, while the other portion of the gas travels through the motor before flowing in the direction of the compression stage.
  • the compressed gas leaves at the central portion in the direction of the chamber for recovering the compressed gas.
  • This structure has a certain number of disadvantages, and particularly because, when the oil for lubricating the various bearings close to the compression zone returns to the casing, the latter flows through the interstices arranged at the motor and therefore comes into contact with the refrigerant gas passing through the motor, which may generate an excessive proportion of oil in the refrigerant gas leaving the compressor.
  • the direct consequence of this excessive proportion of oil in the gas is a loss of heat exchange efficiency of the exchangers situated downstream of the compressor, because the oil droplets contained in the gas tend to be deposited on the exchangers and form a film of oil on the latter.
  • an excessive proportion of oil in the gas may also empty the oil reservoir of the casing, which could ruin the compressor.
  • a known solution for separating the gas and oil flows consists in providing deflectors on the flow path of the refrigerant gas. Because of the changes of direction and the differences of speed due to the presence of the deflectors, the oil is separated from the gaseous flows and falls by gravity into the casing.
  • the degassing of the refrigerant gas limits the flow of oil supply to the bearings, which may cause a risk of damage to the compressor.
  • a known solution consists in arranging radial vent holes in the drive shaft at the various bearings, these vent holes opening on the one hand into the lubrication duct and on the other hand into the wall of the shaft opposite the lubrication orifices.
  • This solution involves arranging, by construction, a pressure gradient helping to expel the gas from the lubrication duct through the vent holes, the pressure gradient however being limited so as not to disrupt the oil flow in the duct. Specifically, too high a pressure gradient could expel oil through the vent holes.
  • the conditions of use of the compressor over its application range involve pressure gradients at the boundaries of the vent holes that vary in large proportions and that therefore greatly change the effectiveness of degassing of the vent holes.
  • the pressure gradient may be inverted and create a vacuum in the lubrication duct, which prevents an expulsion of the gas through the vent holes, which reduces or limits the oil flow leaving the pump on its way to the bearings.
  • the object of the present invention is therefore to remedy these disadvantages.
  • the technical problem at the basis of the invention is the production of a cooling spiral compressor making it possible to control the proportion of oil in the gas leaving the compressor in all the operating conditions of the compressor, while ensuring an effective lubrication of the various guide bearings of the drive shaft.
  • the present invention relates to a cooling spiral compressor comprising:
  • the lubrication duct allows oil to travel from the oil casing to the compression stage in order to lubricate the various guide bearings of the shaft. After all the bearings have been supplied with oil, if there is residual oil, the latter can be carried away in the return duct thanks to the means for placing in communication. Because of the rotation of the shaft, the oil pressed by centrifugation onto the outer portion is forced to flow in the direction of the casing. This residual oil is carried directly to the oil casing without passing through the motor, which therefore makes it possible to limit its contact with the refrigerant gas.
  • the structure of the compressor according to the invention makes it possible to provide a separation of the oil and gas flows that is not linked to the speeds of the gas and hence to the operating conditions of the compressor. Therefore, the structure of the compressor makes it possible to control the proportion of oil in the gas leaving the compressor in all the operating conditions of the latter.
  • the means for placing in communication allow the gas originating from the degassing of the lubrication duct to travel in the return duct to its bottom end irrespective of the flow and speed of rotation of the shaft and the speed of the gases traveling in the compressor. Therefore, the gases originating from the degassing are effectively carried away in all the operating conditions of the compressor.
  • the second end of the return duct opens at the end of the shaft situated on the side of the movable spiral
  • the means for placing in fluidic communication comprising a space delimited by the end of the shaft situated on the side of the movable spiral and the bottom of a housing receiving this end of the shaft.
  • the means for placing in fluidic communication comprise at least one transverse orifice arranged in the shaft whose two ends open respectively into the lubrication and return ducts.
  • the transverse orifice extends radially relative to the shaft.
  • the end of the return duct opening at the end of the shaft situated on the side of the movable spiral opens close to the center of the shaft.
  • the end of the return duct opening, on the side of the casing, into the wall of the shaft is situated substantially at the second end of the shaft.
  • the end of the return duct opening on the side of the casing comprises a vacuum pump designed to accelerate the flow of fluid in the return duct.
  • the diameter of the return duct is less than or equal to the diameter of the lubrication duct.
  • the lubrication duct is inclined relative to the axis of the shaft.
  • the body of the compressor forms an oil collector designed to collect the leakage flows from the bearings situated on the side of the movable spiral, recirculation means being provided to move the oil collected by the collector in the return duct.
  • the recirculation means comprise a duct arranged in the drive shaft opening on the one hand into the return duct and on the other hand into an annular groove arranged in the shaft or in the body of the compressor, a duct supplied with oil from the collector by an oil pump opening into the annular groove.
  • FIG. 1 is a view in longitudinal section of a first compressor.
  • FIG. 2 is a view in longitudinal section of a second compressor.
  • FIG. 3 is a partial enlarged view in cross section of a third compressor.
  • FIG. 4 is a partial view in section along the line IV-IV of FIG. 3 .
  • FIG. 5 is a partial view in longitudinal section of a fourth compressor.
  • FIG. 6 is a view in section along the line B-B of FIG. 5 .
  • FIG. 7 is a view in section along the line C-C of FIG. 6 .
  • FIG. 1 describes a cooling spiral compressor occupying a vertical position.
  • the compressor according to the invention could occupy an inclined position, or a horizontal position, without its structure being modified.
  • the compressor shown in FIG. 1 comprises a sealed enclosure delimited by a shell 2 whose top and bottom ends are closed respectively by a cover 3 and a base 4 .
  • the intermediate portion of the compressor is occupied by a body 5 that delimits two volumes, a suction volume situated below the body 5 and a compression volume placed above the latter.
  • a tube 6 is attached inside which an electric motor is mounted comprising a stator 7 in the center of which a rotor 8 is placed.
  • the tube 6 is for example swaged onto the stator so as to support the motor.
  • the tube 6 rests on a centering part 9 itself attached to the shell 2 .
  • an orifice 10 is arranged with which is associated a coupling 12 for bringing gas to the compressor.
  • This coupling 12 opens into an annular volume 13 arranged between the shell 2 and the tube 6 containing the motor, in the top portion of the motor.
  • the coupling 12 is extended, at the annular volume 13 , by a sleeve 14 passing through this annular space and opening into a top chamber 11 delimited by the tube 6 , containing the coil head of the motor.
  • the sleeve 14 has a bypass opening 15 .
  • the body 5 is used for mounting a gas compression stage 16 .
  • This compression stage comprises a fixed volute 17 fitted with a fixed spiral 18 turned downward, and a movable volute 19 fitted with a spiral 20 turned upward.
  • the two spirals 18 and 20 of the two volutes penetrate one another to arrange variable volume compression chambers 22 .
  • the gas is admitted from the outside, the compression chambers 22 having a variable volume that diminishes from the outside to the inside during the movement of the movable volute 19 relative to the fixed volute 17 , the compressed gas escaping at the center of the volutes via an opening 23 in the direction of a chamber 24 from which it is carried away via a coupling 25 .
  • a shaft 26 is immobilized whose top end is out of alignment in the manner of a crankshaft.
  • This top portion is engaged in a housing delimited by a portion 27 in the shape of a sleeve, that the movable volute 19 comprises.
  • the shaft 26 drives the movable volute that is guided by means of a connecting element 28 in relation to the fixed volute 17 , in an orbital motion.
  • the shaft 26 is guided relative to the other parts by means of a bottom bearing 29 arranged in the centering part 9 , an intermediate bearing 30 arranged in the body 5 and a top bearing 32 arranged between the shaft 26 and the sleeve 27 .
  • the volume containing the top bearing 32 communicates with the chamber 11 through openings 21 arranged in the body 5 .
  • the base 4 delimits a casing 31 containing oil, the oil level being marked by the reference 33 .
  • Immersed in the oil bath is the end of the inlet duct of the pump 34 , which supplies the various bearings with lubrication oil by means of a lubrication duct 35 inclined relative to the axis of the shaft, opening into the end of the latter situated on the side of the movable volute 19 , and by lubrication orifices 36 at the bearings, to lubricate the latter.
  • the lubricating oil may return to the casing by passing through the openings 21 arranged in the body 5 , and in the interstices arranged at the motor, allowing the leakage flow from the bearings 30 , 32 and from the movable volute 19 to flow in the direction of the motor.
  • the thick arrows represent the gas flow and the thin arrows represent the oil flow.
  • the shaft 26 also comprises a return duct 37 for the oil, inclined relative to the axis of the shaft, of which one end opens at the end of the shaft turned toward the movable volute 19 and at the center of the shaft, and of which the other end opens into the peripheral wall of the shaft, in the zone of the latter situated at the end of the motor opposite to the compression volume.
  • Means are provided for placing the lubrication duct 35 and the return duct 37 in fluidic communication. These means for placing in communication comprise a space 38 delimited by the end of the shaft situated on the side of the movable spiral and the bottom of the housing receiving this end of the shaft.
  • the means for placing in fluidic communication also comprise transverse orifices 39 arranged in the shaft, the two ends of each orifice opening respectively into the lubrication duct 35 and return duct 37 .
  • the tube 6 used to support the motor comprises, in its bottom portion, one or more radial orifices 40 that can each be fitted with a diffuser such as a grill 41 .
  • this compressor refrigerant gas impregnated with oil and potentially with liquid particles arrives via the coupling 12 .
  • An important portion of the gas flow passes via the sleeve 14 into the volume delimited by the tube 6 that is above the motor.
  • Another portion of the flow passes the bypass duct 15 into the annular volume 13 to flow directly toward the compression stage 16 .
  • the gas arriving in the volume situated above the motor is mixed with the lubrication oil that flows in the direction of the bottom bearing 29 , particularly from the top bearing 32 and the intermediate bearing 30 .
  • the mixture of gas and lubrication oil travels through the motor to the bottom, carrying away the heat losses of the motor.
  • This passage occurs in particular through a space 42 situated between the rotor and the stator, and via a space 43 situated between the stator and the tube 6 .
  • the mixed flow flowing through the motor arrives in the bottom portion of the motor where the oil flow from the bottom bearing is added.
  • the gas-oil mixture then passes through the radial orifices 40 through the diffusers 41 consisting for example of a metal trellis forming a grill.
  • This trellis allows the gas flow to diffuse all around the motor tube, in the annular volume 13 . Because of the changes of direction and the differences of speed, the oil is separated from the gaseous flow and falls into the casing 31 .
  • the gaseous flow then travels via the annular volume 13 to the compression stage 16 . Separation of the gas and the oil continues during the journey into the annular volume because of gravity and/or the controlled gas speeds and an appropriate separation time.
  • the lubrication duct 35 allows oil to travel from the oil casing 31 to the compression stage in order to lubricate the various guide bearings of the shaft. After supplying all the bearings with oil, the residual oil is carried away in the return duct 37 by means of the space 38 . Because of the rotation of the shaft 26 , the oil pressed by centrifugation onto the outer portion of the return duct is forced to flow in the direction of the casing. This residual oil is carried directly to the oil casing without passing through the motor, which therefore makes it possible to limit its contact with the refrigerant gas.
  • the transverse orifices 39 allow gas originating from the degassing to pass into the return duct 37 to its bottom end irrespective of the flow and speed of rotation of the shaft and the speed of the gases traveling in the compressor.
  • the gas in the return duct can be made to flow because of the fact that the oil pressed by centrifugation leaves free passage to the gas from the bearing of the movable volute to the other end of the return duct. This free passage makes it possible to carry away the gas originating from the degassing of the various bearings in excellent conditions even if there is surplus oil for the supply of the bearings.
  • FIG. 2 represents a variant embodiment of the compressor of FIG. 1 in which the same elements are indicated by the same reference numbers as before.
  • the end of the return duct 37 opening, on the side of the casing 31 , into the wall of the shaft 26 is situated substantially at the second end of the shaft and beyond the bottom bearing 29 .
  • the return duct 37 makes it possible to carry away a considerable flow of oil, while being sure that the latter will return to the casing, irrespective of the flow provided by the pump and the speed of rotation of the shaft.
  • FIGS. 3 and 4 represent a variant embodiment of the compressor of FIG. 2 .
  • the end of the return duct 37 situated on the side of the casing 31 opens into a transverse orifice 39 arranged in the shaft whose two ends open respectively into the lubrication duct 35 and the wall of the shaft.
  • this end of the return duct 37 is fitted with a vacuum pump 44 designed to accelerate the flow of fluid in the return duct.
  • the vacuum pump is formed by a tube comprising a first portion 45 placed longitudinally in the return duct, a second portion 46 perpendicular to the first portion and extending in the transverse orifice 39 radially outward from the first portion, and a third portion 47 perpendicular to the plane defined by the first and second portions and extending from the second portion in a direction opposite to the direction of rotation of the shaft.
  • first and second portions have sections that are respectively less than those of the return duct and of the transverse orifice 39 , in order to allow free passage to a certain quantity of fluid flowing in the return duct and in the transverse orifice.
  • this tube creates a vacuum in the return duct and therefore a suction effect in the latter.
  • the result of this is an acceleration of the fluid that is close to the opening of the tube placed in the return duct, and therefore, step by step the flow of the fluid traveling in the return duct.
  • FIGS. 5 to 7 represent a fourth variant embodiment of the compressor of FIG. 1 .
  • the body 5 of the compressor contains no openings 21 and therefore forms an oil collector designed to collect the leakage flows from the top bearing 32 and intermediate bearing 30 .
  • Recirculation means are provided to carry the oil collected by the collector into the return duct 37 .
  • the recirculation means comprise a duct 50 arranged in the drive shaft 26 and opening on the one hand into the return duct 37 and on the other hand into an annular groove 51 arranged in the body 5 of the compressor.
  • the recirculation means also comprise a duct 52 arranged in the body 5 and opening into the annular groove 51 .
  • the duct 52 is supplied with oil from the collector by an oil pump 53 placed in a housing 54 arranged in the body 5 .
  • the oil pump 53 comprises a first gear wheel 55 placed about the shaft 26 and engaging with a second idler gear wheel 56 .
  • the oil collected in the body 5 is sucked into the housing 54 , then compressed in the spaces arranged between the gear wheels and the body 5 , before being carried away in the duct 52 . Then, the compressed oil flows into the annular groove 51 to be finally taken into the return duct 37 with the aid of the duct 50 .
  • the invention is not limited solely to the embodiments of this compressor described above as examples; on the contrary, it covers all the variant embodiments. Therefore, in particular, the end of the return duct turned toward the compression stage could be blocked off for specific requirements of use. In addition, the coupling 12 could open into the annular volume 13 in the bottom portion of the motor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressor (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

A scroll-type refrigerant compressor includes a drive shaft with an off-axis lubrication conduit which is supplied with oil from an oil pan located in the lower part of the compressor by an oil pump that is disposed at a first end of the shaft. The lubrication conduit has lubrication holes at the different shaft guide bearings. The second end of the shaft is equipped with a device that enables the orbital movement of the moving scroll of the compressor. The aforementioned shaft also includes a return conduit which is inclined in relation to the axis of the shaft and which extends over at least part of the length thereof. One of the ends of the return conduit opens at the wall of the shaft in the area located beyond the rotor on the side of the oil pan. In addition, fluid communication is provided between the lubrication conduit and the return conduit.

Description

The subject of the present invention is a cooling spiral compressor.
A spiral compressor, also known as a scroll compressor, comprises a sealed enclosure delimited by a shell containing a suction volume and a compression volume separated by a compression stage, and placed respectively on the sides of the two ends of the enclosure.
An electric motor is placed in the suction volume, with a stator situated on the outside, mounted fixedly relative to the shell, and a rotor placed in a central position, fixedly attached to a drive shaft or crank shaft. The drive shaft comprises an out-of-alignment lubrication duct extending over the whole length of the latter, supplied with oil contained in a casing situated in the bottom portion of the enclosure by an oil pump placed at a first end of the shaft. The lubrication duct comprises lubrication orifices at the various guide bearings of the shaft.
The compression stage contains a fixed volute fitted with a spiral engaged in a spiral of a movable volute, the two spirals delimiting at least one compression chamber of variable volume. The second end of the drive shaft is fitted with an eccentric driving the movable volute in an orbital motion, to compress the aspirated refrigerant gas.
The shell delimiting the sealed enclosure comprises a refrigerant gas inlet. This inlet opens into the annular volume arranged between the motor and the shell. From a practical point of view, gas arrives from outside and enters this annular space. One portion of the gas is directly sucked in the direction of the compression stage, while the other portion of the gas travels through the motor before flowing in the direction of the compression stage. All the gas arriving at the compression stage either directly, or after passing through the motor, is sucked in by the compression stage, entering at least one compression chamber delimited by the two spirals, the entrance being made at the periphery of the compression stage, and the gas being carried to the center of the spirals gradually as the compression is generated by reducing the volume of the compression chambers, resulting from the movement of the movable volute relative to the fixed volute. The compressed gas leaves at the central portion in the direction of the chamber for recovering the compressed gas.
This structure has a certain number of disadvantages, and particularly because, when the oil for lubricating the various bearings close to the compression zone returns to the casing, the latter flows through the interstices arranged at the motor and therefore comes into contact with the refrigerant gas passing through the motor, which may generate an excessive proportion of oil in the refrigerant gas leaving the compressor. The direct consequence of this excessive proportion of oil in the gas is a loss of heat exchange efficiency of the exchangers situated downstream of the compressor, because the oil droplets contained in the gas tend to be deposited on the exchangers and form a film of oil on the latter.
In addition, an excessive proportion of oil in the gas may also empty the oil reservoir of the casing, which could ruin the compressor.
To remedy these disadvantages, a separation of the gas and oil flows is often used.
A known solution for separating the gas and oil flows consists in providing deflectors on the flow path of the refrigerant gas. Because of the changes of direction and the differences of speed due to the presence of the deflectors, the oil is separated from the gaseous flows and falls by gravity into the casing.
However, the effectiveness of this solution is directly linked to the speeds of the gases. Specifically, when the speeds of the gases are too high, the time for separation of the oil and gas is greatly diminished, which may cause an excessive proportion of oil in the gas and therefore a reduction in the efficiency of the compressor or even a destruction of the latter.
Therefore, this solution for separating the gas and oil flows is not sufficiently effective and reliable in all the application conditions of the compressor.
Another problem encountered in this type of compressor is linked to the degassing of the refrigerant gas contained in the lubrication oil when the latter flows in the lubrication duct. This degassing of the gas in the lubrication duct is a consequence of the centrifugation generated by the rotation of the drive shaft.
In certain conditions of operation of the compressor, the degassing of the refrigerant gas limits the flow of oil supply to the bearings, which may cause a risk of damage to the compressor.
In order to prevent this situation, various solutions for carrying these gases away are proposed.
A known solution consists in arranging radial vent holes in the drive shaft at the various bearings, these vent holes opening on the one hand into the lubrication duct and on the other hand into the wall of the shaft opposite the lubrication orifices. This solution involves arranging, by construction, a pressure gradient helping to expel the gas from the lubrication duct through the vent holes, the pressure gradient however being limited so as not to disrupt the oil flow in the duct. Specifically, too high a pressure gradient could expel oil through the vent holes.
The conditions of use of the compressor over its application range involve pressure gradients at the boundaries of the vent holes that vary in large proportions and that therefore greatly change the effectiveness of degassing of the vent holes. In addition, in some cases, the pressure gradient may be inverted and create a vacuum in the lubrication duct, which prevents an expulsion of the gas through the vent holes, which reduces or limits the oil flow leaving the pump on its way to the bearings.
The object of the present invention is therefore to remedy these disadvantages.
The technical problem at the basis of the invention is the production of a cooling spiral compressor making it possible to control the proportion of oil in the gas leaving the compressor in all the operating conditions of the compressor, while ensuring an effective lubrication of the various guide bearings of the drive shaft.
Accordingly, the present invention relates to a cooling spiral compressor comprising:
    • a sealed enclosure containing a suction volume and a compression volume placed respectively on the side of the two ends of the enclosure on either side of a body, the enclosure comprising a refrigerant gas inlet,
    • an electric motor placed on the suction side having a stator and a rotor fixedly attached to a drive shaft in the form of a crankshaft,
    • the drive shaft comprising an out-of-alignment lubrication duct extending over the whole length of the latter, supplied by oil contained in a casing situated in the bottom portion of the enclosure by an oil pump placed at a first end of the shaft, the lubrication duct comprising lubrication orifices at different guide bearings of the shaft,
    • the second end of the drive shaft being fitted with a device for driving the movable spiral of the compressor in an orbital motion,
      characterized in that the drive shaft comprises a return duct parallel or inclined relative to the axis of the shaft and extending over at least a portion of the length of the shaft, one of the ends of the return duct opening into the wall of the shaft, in the zone of the latter situated beyond the rotor, on the side of the oil casing, means being provided for placing the lubrication and return ducts in fluidic communication.
The lubrication duct allows oil to travel from the oil casing to the compression stage in order to lubricate the various guide bearings of the shaft. After all the bearings have been supplied with oil, if there is residual oil, the latter can be carried away in the return duct thanks to the means for placing in communication. Because of the rotation of the shaft, the oil pressed by centrifugation onto the outer portion is forced to flow in the direction of the casing. This residual oil is carried directly to the oil casing without passing through the motor, which therefore makes it possible to limit its contact with the refrigerant gas.
Accordingly, the structure of the compressor according to the invention makes it possible to provide a separation of the oil and gas flows that is not linked to the speeds of the gas and hence to the operating conditions of the compressor. Therefore, the structure of the compressor makes it possible to control the proportion of oil in the gas leaving the compressor in all the operating conditions of the latter.
In addition, the means for placing in communication allow the gas originating from the degassing of the lubrication duct to travel in the return duct to its bottom end irrespective of the flow and speed of rotation of the shaft and the speed of the gases traveling in the compressor. Therefore, the gases originating from the degassing are effectively carried away in all the operating conditions of the compressor.
In addition, because the residual oil is pressed by centrifugation in the outer portion of the return duct, the latter leaves a free passage for the gas to the bottom end of the return duct. This free passage makes it possible to carry away the gas originating from the degassing in excellent conditions even if there is surplus oil for supplying the bearings.
Advantageously, the second end of the return duct opens at the end of the shaft situated on the side of the movable spiral, the means for placing in fluidic communication comprising a space delimited by the end of the shaft situated on the side of the movable spiral and the bottom of a housing receiving this end of the shaft.
According to another feature of the invention, the means for placing in fluidic communication comprise at least one transverse orifice arranged in the shaft whose two ends open respectively into the lubrication and return ducts.
Advantageously, the transverse orifice extends radially relative to the shaft.
According to yet another feature of the invention, the end of the return duct opening at the end of the shaft situated on the side of the movable spiral opens close to the center of the shaft.
Advantageously, the end of the return duct opening, on the side of the casing, into the wall of the shaft is situated substantially at the second end of the shaft.
According to another feature of the invention, the end of the return duct opening on the side of the casing comprises a vacuum pump designed to accelerate the flow of fluid in the return duct.
Preferably, the diameter of the return duct is less than or equal to the diameter of the lubrication duct.
According to another feature of the invention, the lubrication duct is inclined relative to the axis of the shaft.
According to yet another feature of the invention, the body of the compressor forms an oil collector designed to collect the leakage flows from the bearings situated on the side of the movable spiral, recirculation means being provided to move the oil collected by the collector in the return duct.
Advantageously, the recirculation means comprise a duct arranged in the drive shaft opening on the one hand into the return duct and on the other hand into an annular groove arranged in the shaft or in the body of the compressor, a duct supplied with oil from the collector by an oil pump opening into the annular groove.
In any case, the invention will be well understood with the aid of the following description, with reference to the appended schematic drawing, representing, as nonlimiting examples, several embodiments of this compressor.
FIG. 1 is a view in longitudinal section of a first compressor.
FIG. 2 is a view in longitudinal section of a second compressor.
FIG. 3 is a partial enlarged view in cross section of a third compressor.
FIG. 4 is a partial view in section along the line IV-IV of FIG. 3.
FIG. 5 is a partial view in longitudinal section of a fourth compressor.
FIG. 6 is a view in section along the line B-B of FIG. 5.
FIG. 7 is a view in section along the line C-C of FIG. 6.
FIG. 1 describes a cooling spiral compressor occupying a vertical position. However, the compressor according to the invention, could occupy an inclined position, or a horizontal position, without its structure being modified.
The compressor shown in FIG. 1 comprises a sealed enclosure delimited by a shell 2 whose top and bottom ends are closed respectively by a cover 3 and a base 4. The intermediate portion of the compressor is occupied by a body 5 that delimits two volumes, a suction volume situated below the body 5 and a compression volume placed above the latter. Onto the body a tube 6 is attached inside which an electric motor is mounted comprising a stator 7 in the center of which a rotor 8 is placed. The tube 6 is for example swaged onto the stator so as to support the motor. At its bottom end, the tube 6 rests on a centering part 9 itself attached to the shell 2. In the shell 2 an orifice 10 is arranged with which is associated a coupling 12 for bringing gas to the compressor. This coupling 12 opens into an annular volume 13 arranged between the shell 2 and the tube 6 containing the motor, in the top portion of the motor.
The coupling 12 is extended, at the annular volume 13, by a sleeve 14 passing through this annular space and opening into a top chamber 11 delimited by the tube 6, containing the coil head of the motor. In the annular volume 13, the sleeve 14 has a bypass opening 15.
The body 5 is used for mounting a gas compression stage 16. This compression stage comprises a fixed volute 17 fitted with a fixed spiral 18 turned downward, and a movable volute 19 fitted with a spiral 20 turned upward. The two spirals 18 and 20 of the two volutes penetrate one another to arrange variable volume compression chambers 22. The gas is admitted from the outside, the compression chambers 22 having a variable volume that diminishes from the outside to the inside during the movement of the movable volute 19 relative to the fixed volute 17, the compressed gas escaping at the center of the volutes via an opening 23 in the direction of a chamber 24 from which it is carried away via a coupling 25.
Onto the rotor 8 a shaft 26 is immobilized whose top end is out of alignment in the manner of a crankshaft. This top portion is engaged in a housing delimited by a portion 27 in the shape of a sleeve, that the movable volute 19 comprises. When it is rotated by the motor, the shaft 26 drives the movable volute that is guided by means of a connecting element 28 in relation to the fixed volute 17, in an orbital motion.
The shaft 26 is guided relative to the other parts by means of a bottom bearing 29 arranged in the centering part 9, an intermediate bearing 30 arranged in the body 5 and a top bearing 32 arranged between the shaft 26 and the sleeve 27. The volume containing the top bearing 32 communicates with the chamber 11 through openings 21 arranged in the body 5.
The base 4 delimits a casing 31 containing oil, the oil level being marked by the reference 33. Immersed in the oil bath is the end of the inlet duct of the pump 34, which supplies the various bearings with lubrication oil by means of a lubrication duct 35 inclined relative to the axis of the shaft, opening into the end of the latter situated on the side of the movable volute 19, and by lubrication orifices 36 at the bearings, to lubricate the latter.
In the top portion, the lubricating oil may return to the casing by passing through the openings 21 arranged in the body 5, and in the interstices arranged at the motor, allowing the leakage flow from the bearings 30, 32 and from the movable volute 19 to flow in the direction of the motor.
In FIG. 1, the thick arrows represent the gas flow and the thin arrows represent the oil flow.
According to an important feature of the invention, the shaft 26 also comprises a return duct 37 for the oil, inclined relative to the axis of the shaft, of which one end opens at the end of the shaft turned toward the movable volute 19 and at the center of the shaft, and of which the other end opens into the peripheral wall of the shaft, in the zone of the latter situated at the end of the motor opposite to the compression volume.
Means are provided for placing the lubrication duct 35 and the return duct 37 in fluidic communication. These means for placing in communication comprise a space 38 delimited by the end of the shaft situated on the side of the movable spiral and the bottom of the housing receiving this end of the shaft.
The means for placing in fluidic communication also comprise transverse orifices 39 arranged in the shaft, the two ends of each orifice opening respectively into the lubrication duct 35 and return duct 37.
The tube 6 used to support the motor comprises, in its bottom portion, one or more radial orifices 40 that can each be fitted with a diffuser such as a grill 41.
The operation of this compressor is as follows: refrigerant gas impregnated with oil and potentially with liquid particles arrives via the coupling 12. An important portion of the gas flow passes via the sleeve 14 into the volume delimited by the tube 6 that is above the motor. Another portion of the flow passes the bypass duct 15 into the annular volume 13 to flow directly toward the compression stage 16. The gas arriving in the volume situated above the motor is mixed with the lubrication oil that flows in the direction of the bottom bearing 29, particularly from the top bearing 32 and the intermediate bearing 30. The mixture of gas and lubrication oil travels through the motor to the bottom, carrying away the heat losses of the motor. This passage occurs in particular through a space 42 situated between the rotor and the stator, and via a space 43 situated between the stator and the tube 6. The mixed flow flowing through the motor arrives in the bottom portion of the motor where the oil flow from the bottom bearing is added. The gas-oil mixture then passes through the radial orifices 40 through the diffusers 41 consisting for example of a metal trellis forming a grill. This trellis allows the gas flow to diffuse all around the motor tube, in the annular volume 13. Because of the changes of direction and the differences of speed, the oil is separated from the gaseous flow and falls into the casing 31. The gaseous flow then travels via the annular volume 13 to the compression stage 16. Separation of the gas and the oil continues during the journey into the annular volume because of gravity and/or the controlled gas speeds and an appropriate separation time.
The lubrication duct 35 allows oil to travel from the oil casing 31 to the compression stage in order to lubricate the various guide bearings of the shaft. After supplying all the bearings with oil, the residual oil is carried away in the return duct 37 by means of the space 38. Because of the rotation of the shaft 26, the oil pressed by centrifugation onto the outer portion of the return duct is forced to flow in the direction of the casing. This residual oil is carried directly to the oil casing without passing through the motor, which therefore makes it possible to limit its contact with the refrigerant gas.
In addition, the transverse orifices 39 allow gas originating from the degassing to pass into the return duct 37 to its bottom end irrespective of the flow and speed of rotation of the shaft and the speed of the gases traveling in the compressor. The gas in the return duct can be made to flow because of the fact that the oil pressed by centrifugation leaves free passage to the gas from the bearing of the movable volute to the other end of the return duct. This free passage makes it possible to carry away the gas originating from the degassing of the various bearings in excellent conditions even if there is surplus oil for the supply of the bearings.
FIG. 2 represents a variant embodiment of the compressor of FIG. 1 in which the same elements are indicated by the same reference numbers as before. In this compressor, the end of the return duct 37 opening, on the side of the casing 31, into the wall of the shaft 26 is situated substantially at the second end of the shaft and beyond the bottom bearing 29.
In this case, the return duct 37 makes it possible to carry away a considerable flow of oil, while being sure that the latter will return to the casing, irrespective of the flow provided by the pump and the speed of rotation of the shaft.
FIGS. 3 and 4 represent a variant embodiment of the compressor of FIG. 2. In this compressor, the end of the return duct 37 situated on the side of the casing 31 opens into a transverse orifice 39 arranged in the shaft whose two ends open respectively into the lubrication duct 35 and the wall of the shaft.
In addition, this end of the return duct 37 is fitted with a vacuum pump 44 designed to accelerate the flow of fluid in the return duct. The vacuum pump is formed by a tube comprising a first portion 45 placed longitudinally in the return duct, a second portion 46 perpendicular to the first portion and extending in the transverse orifice 39 radially outward from the first portion, and a third portion 47 perpendicular to the plane defined by the first and second portions and extending from the second portion in a direction opposite to the direction of rotation of the shaft.
It should be noted that the first and second portions have sections that are respectively less than those of the return duct and of the transverse orifice 39, in order to allow free passage to a certain quantity of fluid flowing in the return duct and in the transverse orifice.
During the rotation of the shaft 26, whose direction of rotation is shown by the arrow ω in FIG. 4, the structure of this tube creates a vacuum in the return duct and therefore a suction effect in the latter. The result of this is an acceleration of the fluid that is close to the opening of the tube placed in the return duct, and therefore, step by step the flow of the fluid traveling in the return duct.
The presence of this vacuum pump therefore helps with the return of oil to the casing.
FIGS. 5 to 7 represent a fourth variant embodiment of the compressor of FIG. 1.
According to this variant embodiment, the body 5 of the compressor contains no openings 21 and therefore forms an oil collector designed to collect the leakage flows from the top bearing 32 and intermediate bearing 30.
Recirculation means are provided to carry the oil collected by the collector into the return duct 37. The recirculation means comprise a duct 50 arranged in the drive shaft 26 and opening on the one hand into the return duct 37 and on the other hand into an annular groove 51 arranged in the body 5 of the compressor. The recirculation means also comprise a duct 52 arranged in the body 5 and opening into the annular groove 51. The duct 52 is supplied with oil from the collector by an oil pump 53 placed in a housing 54 arranged in the body 5.
The oil pump 53 comprises a first gear wheel 55 placed about the shaft 26 and engaging with a second idler gear wheel 56.
During the rotation of the shaft 26, and therefore of the gear wheels 55 and 56, the oil collected in the body 5 is sucked into the housing 54, then compressed in the spaces arranged between the gear wheels and the body 5, before being carried away in the duct 52. Then, the compressed oil flows into the annular groove 51 to be finally taken into the return duct 37 with the aid of the duct 50.
As it goes without saying, the invention is not limited solely to the embodiments of this compressor described above as examples; on the contrary, it covers all the variant embodiments. Therefore, in particular, the end of the return duct turned toward the compression stage could be blocked off for specific requirements of use. In addition, the coupling 12 could open into the annular volume 13 in the bottom portion of the motor.
In addition, this arrangement could be associated with compressor structures different from those described, particularly with compressors having different gas circuits without for all that departing from the context of the invention.

Claims (11)

1. A cooling spiral compressor, comprising:
a sealed enclosure containing a suction volume and a compression volume placed respectively on the side of the two ends of the enclosure on either side of a body, the enclosure comprising a refrigerant gas inlet,
an electric motor placed on the suction side having a stator and a rotor fixedly attached to a drive shaft in the form of a crankshaft,
the drive shaft comprising an out-of-alignment lubrication duct extending over the whole length of the drive shaft, supplied by oil contained in a casing situated in the bottom portion of the enclosure by an oil pump placed at a first end of the shaft, the lubrication duct comprising lubrication orifices at different guide bearings of the shaft,
the second end of the drive shaft being fitted with a device for driving the movable spiral of the compressor in an orbital motion,
wherein the drive shaft comprises a return duct parallel or inclined relative to the axis of the shaft and extending over at least a portion of the length of the shaft, one of the ends of the return duct opening into the wall of the shaft, in the zone of the shaft situated beyond the rotor, on the side of the oil casing, means being provided for placing the lubrication and return ducts in fluidic communication.
2. The compressor as claimed in claim 1, wherein the second end of the return duct opens at the end of the shaft situated on the side of the movable spiral, the means for placing in fluidic communication comprising a space delimited by the end of the shaft situated on the side of the movable spiral and the bottom of a housing receiving this end of the shaft.
3. The compressor as claimed in claim 2, wherein the end of the return duct opening at the end of the shaft situated on the side of the movable spiral opens close to the center of the shaft.
4. The compressor as claimed in claim 1, wherein the means for placing in fluidic communication comprise at least one transverse orifice arranged in the shaft whose two ends open respectively into the lubrication and return ducts.
5. The compressor as claimed in claim 4, wherein the transverse orifice extends radially relative to the shaft.
6. The compressor as claimed in claim 1, wherein the end of the return duct opening, on the side of the casing, into the wall of the shaft is situated substantially at the second end of the shaft.
7. The compressor as claimed in claim 1, wherein the end of the return duct opening on the side of the casing comprises a vacuum pump designed to accelerate the flow of fluid in the return duct.
8. The compressor as claimed in claim 1, wherein the diameter of the return duct is less than or equal to the diameter of the lubrication duct.
9. The compressor as claimed in claim 1, wherein the lubrication duct is inclined relative to the axis of the shaft.
10. The compressor as claimed in claim 1, wherein the body of the compressor forms an oil collector designed to collect the leakage flows from the bearings situated on the side of the movable spiral, recirculation means being provided to move the oil collected by the collector in the return duct.
11. The compressor as claimed in claim 10, wherein the recirculation means comprise a duct arranged in the drive shaft opening on the one hand into the return duct and on the other hand into an annular groove arranged in the shaft or in the body of the compressor, a duct supplied with oil from the collector by an oil pump opening into the annular groove.
US11/920,979 2005-05-23 2006-05-23 Scroll-type refrigerant compressor having fluid communication between lubrication duct and return duct Expired - Fee Related US7670120B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0505153A FR2885966B1 (en) 2005-05-23 2005-05-23 SPIRAL REFRIGERATING COMPRESSOR
FR0505153 2005-05-23
PCT/FR2006/001175 WO2006125908A1 (en) 2005-05-23 2006-05-23 Scroll-type refrigerant compressor

Publications (2)

Publication Number Publication Date
US20090041602A1 US20090041602A1 (en) 2009-02-12
US7670120B2 true US7670120B2 (en) 2010-03-02

Family

ID=35518088

Family Applications (2)

Application Number Title Priority Date Filing Date
US11/920,979 Expired - Fee Related US7670120B2 (en) 2005-05-23 2006-05-23 Scroll-type refrigerant compressor having fluid communication between lubrication duct and return duct
US11/918,717 Expired - Fee Related US7708536B2 (en) 2005-05-23 2006-05-23 Scroll-type refrigerant compressor having fluid flowing from gas inlet to motor winding end chamber through intermediate jacket

Family Applications After (1)

Application Number Title Priority Date Filing Date
US11/918,717 Expired - Fee Related US7708536B2 (en) 2005-05-23 2006-05-23 Scroll-type refrigerant compressor having fluid flowing from gas inlet to motor winding end chamber through intermediate jacket

Country Status (8)

Country Link
US (2) US7670120B2 (en)
EP (1) EP1886024B1 (en)
KR (1) KR100938798B1 (en)
CN (2) CN100575706C (en)
AT (1) ATE437307T1 (en)
DE (2) DE602006007987D1 (en)
FR (1) FR2885966B1 (en)
WO (2) WO2006125908A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220106952A1 (en) * 2019-04-03 2022-04-07 Hitachi-Johnson Controls Air Conditioning, Inc. Compressor and air-conditioner
US11446619B2 (en) 2017-10-24 2022-09-20 Dow Global Technologies Llc Pulsed compression reactors and methods for their operation
US20250129783A1 (en) * 2023-10-20 2025-04-24 Trane International Inc. Lubrication system for compressors

Families Citing this family (53)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007110378A1 (en) * 2006-03-24 2007-10-04 Siemens Aktiengesellschaft Compressor unit and assembly method
KR100869929B1 (en) * 2007-02-23 2008-11-24 엘지전자 주식회사 Scroll compressor
FR2915534B1 (en) * 2007-04-25 2009-05-29 Danfoss Commercial Compressors METHOD FOR ASSEMBLING A REFRIGERATING COMPRESSOR
FR2916813B1 (en) 2007-05-29 2013-02-08 Danfoss Commercial Compressors SPIRAL REFRIGERATOR COMPRESSOR WITH VARIABLE SPEED
US7878780B2 (en) * 2008-01-17 2011-02-01 Bitzer Kuhlmaschinenbau Gmbh Scroll compressor suction flow path and bearing arrangement features
US8133043B2 (en) 2008-10-14 2012-03-13 Bitzer Scroll, Inc. Suction duct and scroll compressor incorporating same
FR2942656B1 (en) 2009-02-27 2013-04-12 Danfoss Commercial Compressors DEVICE FOR SEPARATING LUBRICANT FROM A LUBRICANT-REFRIGERATING GAS MIXTURE
WO2012028098A1 (en) * 2010-08-31 2012-03-08 Emerson Climate Technologies (Suzhou) Research & Development Co., Ltd. Scroll compressor
BRPI1103384A2 (en) * 2011-07-29 2013-07-30 Whirlpool Sa pumping system and shaft for oil pumping system for airtight compressors and compressor comprising the system and / or shaft
CN102305208A (en) * 2011-08-30 2012-01-04 刘明辉 Oil pump for reciprocating variable speed sealing compressor
KR101285617B1 (en) * 2011-09-09 2013-07-23 엘지전자 주식회사 Scroll compressor
US8814537B2 (en) * 2011-09-30 2014-08-26 Emerson Climate Technologies, Inc. Direct-suction compressor
FR2984425B1 (en) 2011-12-14 2014-05-16 Danfoss Commercial Compressors OIL INJECTION DEVICE FOR SPIRAL REFRIGERATION COMPRESSOR WITH VARIABLE SPEED
FR2984424B1 (en) 2011-12-14 2018-06-01 Danfoss Commercial Compressors SPIRAL REFRIGERATOR COMPRESSOR WITH VARIABLE SPEED
US9441631B2 (en) 2012-03-23 2016-09-13 Bitzer Kuehlmaschinenbau Gmbh Suction duct with heat-staked screen
US9458850B2 (en) 2012-03-23 2016-10-04 Bitzer Kuehlmaschinenbau Gmbh Press-fit bearing housing with non-cylindrical diameter
US9039384B2 (en) * 2012-03-23 2015-05-26 Bitzer Kuehlmaschinenbau Gmbh Suction duct with adjustable diametric fit
US8920139B2 (en) 2012-03-23 2014-12-30 Bitzer Kuehlmaschinenbau Gmbh Suction duct with stabilizing ribs
US9181949B2 (en) 2012-03-23 2015-11-10 Bitzer Kuehlmaschinenbau Gmbh Compressor with oil return passage formed between motor and shell
FR2989433B1 (en) * 2012-04-16 2018-10-12 Danfoss Commercial Compressors SPIRAL COMPRESSOR
JP5931563B2 (en) * 2012-04-25 2016-06-08 アネスト岩田株式会社 Scroll expander
CN103452857B (en) * 2012-05-31 2015-08-05 基益企业股份有限公司 Electric water pump
US9689386B2 (en) 2012-07-31 2017-06-27 Bitzer Kuehlmaschinenbau Gmbh Method of active oil management for multiple scroll compressors
US10495089B2 (en) 2012-07-31 2019-12-03 Bitzer Kuehlmashinenbau GmbH Oil equalization configuration for multiple compressor systems containing three or more compressors
US10634137B2 (en) 2012-07-31 2020-04-28 Bitzer Kuehlmaschinenbau Gmbh Suction header arrangement for oil management in multiple-compressor systems
EP2909480B1 (en) 2012-09-13 2020-06-24 Emerson Climate Technologies, Inc. Compressor assembly with directed suction
FR2998340A1 (en) * 2012-11-19 2014-05-23 Danfoss Commercial Compressors SPIRAL COMPRESSOR WITH VARIABLE SPEED.
CN103967784B (en) * 2013-01-29 2019-03-22 艾默生环境优化技术(苏州)有限公司 Compressor with a compressor housing having a plurality of compressor blades
US9051934B2 (en) 2013-02-28 2015-06-09 Bitzer Kuehlmaschinenbau Gmbh Apparatus and method for oil equalization in multiple-compressor systems
CN104704241B (en) * 2013-03-13 2017-05-10 艾默生环境优化技术有限公司 Lower Bearing Assembly For Scroll Compressor
JP2015036525A (en) * 2013-08-12 2015-02-23 ダイキン工業株式会社 Scroll compressor
CN105443377A (en) * 2014-06-10 2016-03-30 丹佛斯（天津）有限公司 Scroll compressor
EP3232061B1 (en) * 2014-12-12 2019-01-30 Daikin Industries, Ltd. Compressor
CN106151047B (en) * 2015-04-24 2019-11-15 艾默生环境优化技术(苏州)有限公司 Scroll compressor and drive shaft for scroll compressor
WO2016169348A1 (en) * 2015-04-24 2016-10-27 艾默生环境优化技术(苏州)有限公司 Scroll compressor and driving shaft for scroll compressor
US11078913B2 (en) * 2015-06-30 2021-08-03 Bitzer Kuehlmaschinenbau Gmbh Two-piece suction fitting
US9939179B2 (en) 2015-12-08 2018-04-10 Bitzer Kuehlmaschinenbau Gmbh Cascading oil distribution system
US10760831B2 (en) 2016-01-22 2020-09-01 Bitzer Kuehlmaschinenbau Gmbh Oil distribution in multiple-compressor systems utilizing variable speed
CN112424475B (en) * 2018-07-20 2022-09-02 三菱电机株式会社 Compressor
KR102546708B1 (en) * 2018-11-20 2023-06-22 삼성전자주식회사 A compressor and electronic device using the same
KR20200085559A (en) * 2019-01-07 2020-07-15 엘지전자 주식회사 Motor operated compressor
US11236748B2 (en) 2019-03-29 2022-02-01 Emerson Climate Technologies, Inc. Compressor having directed suction
US11767838B2 (en) * 2019-06-14 2023-09-26 Copeland Lp Compressor having suction fitting
FR3102812B1 (en) 2019-11-06 2021-11-19 Danfoss Commercial Compressors Scroll compressor with a force-mounted motor and a vertically central suction inlet
CN113123972B (en) 2019-12-31 2023-06-06 丹佛斯（天津）有限公司 Oil pump and scroll compressor
CN211737452U (en) * 2020-02-21 2020-10-23 艾默生环境优化技术(苏州)有限公司 Compressor with a compressor housing having a plurality of compressor blades
US11421922B2 (en) * 2020-04-22 2022-08-23 Haier Us Appliance Solutions, Inc. Heat dissipation assembly for a linear compressor
US11248605B1 (en) 2020-07-28 2022-02-15 Emerson Climate Technologies, Inc. Compressor having shell fitting
FR3114623B1 (en) * 2020-09-29 2022-09-09 Danfoss Commercial Compressors Scroll compressor with oil injection system
US11619228B2 (en) 2021-01-27 2023-04-04 Emerson Climate Technologies, Inc. Compressor having directed suction
US20250067265A1 (en) * 2021-12-31 2025-02-27 Danfoss (Tianjin) Ltd. Scroll compressor
US12180966B2 (en) 2022-12-22 2024-12-31 Copeland Lp Compressor with funnel assembly
CN117189614B (en) * 2023-09-28 2025-05-06 比泽尔制冷技术（中国）有限公司 Scroll compressor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4875840A (en) 1988-05-12 1989-10-24 Tecumseh Products Company Compressor lubrication system with vent
US5240389A (en) * 1991-07-26 1993-08-31 Kabushiki Kaisha Toshiba Scroll type compressor
JP2001065474A (en) * 1999-08-27 2001-03-16 Mitsui Seiki Kogyo Co Ltd Bearing lubrication system for oilless scroll compressors
US20010026766A1 (en) 1998-12-14 2001-10-04 Toshiyuki Terai Scroll compressor
US6599100B2 (en) * 2000-09-20 2003-07-29 Hitachi, Ltd. Closed type motor-operated compressor

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2718666B2 (en) * 1986-07-21 1998-02-25 株式会社日立製作所 Oil supply device for scroll fluid machine
US4877381A (en) * 1988-05-12 1989-10-31 Tecumseh Products Company Compressor shaft collar through port for pressure equalization between fluid pockets
US4928503A (en) * 1988-07-15 1990-05-29 American Standard Inc. Scroll apparatus with pressure regulation
JPH0765578B2 (en) * 1988-12-07 1995-07-19 三菱電機株式会社 Scroll compressor
JPH109160A (en) * 1996-06-24 1998-01-13 Daikin Ind Ltd Scroll compressor
US5885066A (en) * 1997-02-26 1999-03-23 Matsushita Electric Industrial Co., Ltd. Scroll compressor having oil bores formed through the crank shaft
JP2004104895A (en) * 2002-09-09 2004-04-02 Hitachi Ltd Compressor drive device and refrigeration air conditioner
ES2690275T3 (en) * 2000-10-31 2018-11-20 Jfe Steel Corporation High strength hot rolled steel sheet and method for manufacturing it
DE10065821A1 (en) * 2000-12-22 2002-07-11 Bitzer Kuehlmaschinenbau Gmbh compressor
JP2002295380A (en) * 2001-03-29 2002-10-09 Mitsubishi Electric Corp Horizontal scroll compressor
FR2830292B1 (en) * 2001-09-28 2003-12-19 Danfoss Maneurop S A LOW PRESSURE GAS CIRCUIT FOR A COMPRESSOR
DE10248926B4 (en) * 2002-10-15 2004-11-11 Bitzer Kühlmaschinenbau Gmbh compressor
US7311501B2 (en) * 2003-02-27 2007-12-25 American Standard International Inc. Scroll compressor with bifurcated flow pattern
JP4175148B2 (en) * 2003-03-12 2008-11-05 松下電器産業株式会社 Hermetic compressor
JP4440564B2 (en) * 2003-06-12 2010-03-24 パナソニック株式会社 Scroll compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4875840A (en) 1988-05-12 1989-10-24 Tecumseh Products Company Compressor lubrication system with vent
EP0341408A2 (en) 1988-05-12 1989-11-15 Tecumseh Products Company Compressor lubrication system with vent
US5240389A (en) * 1991-07-26 1993-08-31 Kabushiki Kaisha Toshiba Scroll type compressor
US20010026766A1 (en) 1998-12-14 2001-10-04 Toshiyuki Terai Scroll compressor
JP2001065474A (en) * 1999-08-27 2001-03-16 Mitsui Seiki Kogyo Co Ltd Bearing lubrication system for oilless scroll compressors
US6599100B2 (en) * 2000-09-20 2003-07-29 Hitachi, Ltd. Closed type motor-operated compressor

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11446619B2 (en) 2017-10-24 2022-09-20 Dow Global Technologies Llc Pulsed compression reactors and methods for their operation
US11925923B2 (en) 2017-10-24 2024-03-12 Dow Global Technologies Llc Pulsed compression reactors and methods for their operation
US20220106952A1 (en) * 2019-04-03 2022-04-07 Hitachi-Johnson Controls Air Conditioning, Inc. Compressor and air-conditioner
US12025133B2 (en) * 2019-04-03 2024-07-02 Hitachi-Johnson Controls Air Conditioning, Inc. Compressor and air-conditioner
US20250129783A1 (en) * 2023-10-20 2025-04-24 Trane International Inc. Lubrication system for compressors
US12473920B2 (en) * 2023-10-20 2025-11-18 Trane International Inc. Lubrication system for compressors

Also Published As

Publication number Publication date
CN101223364A (en) 2008-07-16
US7708536B2 (en) 2010-05-04
US20090035168A1 (en) 2009-02-05
WO2006125908A1 (en) 2006-11-30
US20090041602A1 (en) 2009-02-12
FR2885966A1 (en) 2006-11-24
CN100575706C (en) 2009-12-30
DE602006007987D1 (en) 2009-09-03
EP1886024A1 (en) 2008-02-13
DE112006001283T5 (en) 2008-04-10
WO2006125909A1 (en) 2006-11-30
FR2885966B1 (en) 2011-01-14
DE112006001283B4 (en) 2014-12-11
ATE437307T1 (en) 2009-08-15
EP1886024B1 (en) 2009-07-22
CN101223365A (en) 2008-07-16
KR100938798B1 (en) 2010-01-27
KR20080011443A (en) 2008-02-04
CN101223364B (en) 2012-08-29

Similar Documents

Publication Publication Date Title
US7670120B2 (en) Scroll-type refrigerant compressor having fluid communication between lubrication duct and return duct
CN208138137U (en) Compressor
JP6297760B2 (en) Blow-by gas drive pump device
US7476090B2 (en) Vented turbocharger center housing and method
KR0126627Y1 (en) Oil shield
US4632650A (en) Vacuum pump having an evacuated gear chamber
CN114857012B (en) Compressor oil return structure, compressor and air conditioner
EP1519053A2 (en) A submerged pump having a bearing lubricated by discharged fluid
JP2008008285A (en) Compressor
WO2018130134A1 (en) Compressor
WO2021011816A1 (en) Air/oil separator
CN205895603U (en) Rotor type compressor
JPH0544667A (en) Sealed type scroll compressor
US11415022B2 (en) Oil console equipment, rotary machine provided with oil console equipment, and method for recovering lubrication oil contained in exhaust gas
RU2610974C2 (en) Lubricating fluid separation device, gas compression device, containing said separation device and separation tank for compression device
CN100520075C (en) Compressor for cooling fluid
CN113904478B (en) Motor element, compressor and air conditioner
WO2019064883A1 (en) Oil separator
CN111237189B (en) Scroll compressor with seal-oil cut-off structure
CN109306957B (en) Compressor with a compressor body having a rotor with a rotor shaft
CN109386467B (en) Oil separation device and horizontal compressor
JP4638313B2 (en) Hermetic rotary compressor
CN113530797A (en) Oil separator, compressor unit spare and heat exchange equipment
US7357237B2 (en) Clutch transmission and method for lubricating and cooling the same
CN113700650B (en) Compressor and air conditioner with same

Legal Events

Date Code Title Description
AS Assignment

Owner name: DANFOSS COMMERCIAL COMPRESSORS, FRANCE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:GINIES, PIERRE;GENEVOIS, DAVID;DE BERNARDI, JEAN;REEL/FRAME:020319/0825

Effective date: 20071218

Owner name: DANFOSS COMMERCIAL COMPRESSORS,FRANCE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:GINIES, PIERRE;GENEVOIS, DAVID;DE BERNARDI, JEAN;REEL/FRAME:020319/0825

Effective date: 20071218

FPAY Fee payment

Year of fee payment: 4

FEPP Fee payment procedure

Free format text: MAINTENANCE FEE REMINDER MAILED (ORIGINAL EVENT CODE: REM.)

LAPS Lapse for failure to pay maintenance fees

Free format text: PATENT EXPIRED FOR FAILURE TO PAY MAINTENANCE FEES (ORIGINAL EVENT CODE: EXP.)

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

FP Lapsed due to failure to pay maintenance fee

Effective date: 20180302